JP2006132550A - Continuously variable transmission assembling structure and its method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a continuously variable transmission assembling structure for allowing after-assembly of an output gear and a ball bearing on a driven shaft without giving overload to the bearing supporting the driven shaft at one end when using the ball bearing for supporting the driven shaft at the other end. <P>SOLUTION: The output gear 27a is fixed to one end of the driven shaft 20 meshing with a ring gear 31 of a differential device 30. The output gear 27a is formed on the outer periphery of a gear sleeve 27, where a cylindrical extension portion 27b with no gear portion is formed at one axial end of the gear sleeve 27 and the ball bearing 26 with its outer diameter larger than the tooth bottom diameter of the output gear is fitted and fixed to the outer periphery of the extension portion. After the driven shaft 20 and the differential device 30 are assembled on a transmission case, the gear sleeve 27 is spline-fitted to the driven shaft 20, the output gear meshes with the ring gear of the differential device, and a lock nut 28 is fastened to the shaft end of the driven shaft to fix the gear sleeve 27. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

The present invention relates to an assembling structure and assembling method for a continuously variable transmission, and more particularly to a structure and a method for fixing an output gear and a ball bearing meshing with a ring gear or a reduction gear of a differential device at one end of a driven shaft.

In general, in a belt-type continuously variable transmission, power input from an engine is transmitted to an input shaft via a torque converter, and is transmitted from the input shaft to a differential device via a drive pulley, a V-belt, and a driven pulley. Is driven.
When power is transmitted from the driven pulley to the differential device, the output gear is integrally formed or fixed to the end of the driven shaft that supports the driven pulley, and the output gear is engaged with the ring gear of the differential device to transmit power. Is going. A reduction gear may be interposed between the driven shaft and the differential device.

A continuously variable transmission having such a transmission path is disclosed in Patent Document 1. The continuously variable transmission has a three-axis structure including a first shaft that supports a driving pulley of a belt-type continuously variable transmission, a second shaft that supports a driven pulley, and a third shaft of a differential device. Both ends of the driven shaft as the second shaft are supported by roller bearings. The output gear is splined to one end of the driven shaft, and the output gear is fixed to the driven shaft by pressing the output gear axially with a lock nut through the inner race of the roller bearing.

FIG. 6 shows the support structure of the driven shaft described in Patent Document 1.
A cylindrical output gear 101 is spline fitted to a spline portion 100a formed at one end of the driven shaft 100, and an inner race 102a of the roller bearing 102 is fitted to the cylindrical portion 100b of the driven shaft 100 following the output gear 101. Further, the lock nut 103 is fastened to the threaded portion 100c of the shaft end of the driven shaft 100 to press the output gear 101 and the inner race 102a in the axial direction, and the end surface of the output gear 101 is attached to the driven shaft 100. It is pressed against the part 104 and fixed. The outer race 102 b of the roller bearing 102 is fitted and held in the transmission case 105. The output gear 101 meshes with a ring gear 106 of a differential device.

Since the inner race 102a of the roller bearing 102 does not need to be press-fitted into the cylindrical portion 100b of the driven shaft 100, the other end side of the driven shaft 100 is supported when the roller bearing 102 is incorporated into the driven shaft 100. There is no heavy load on the bearing. However, the roller bearing 102 has a larger rotation loss than the ball bearing, is expensive, and requires an axial space.

Thus, it is conceivable to use a ball bearing instead of the roller bearing 102. However, since it is necessary to fit and fix the inner race of the ball bearing to the driven shaft, a large axial load is applied to the bearing (roller bearing or ball bearing) that supports the other end of the driven shaft. May damage it. Therefore, the ball bearing must be fitted and fixed to the driven shaft before the driven shaft is incorporated into the transmission case.

By the way, in order to obtain a large reduction ratio, an output gear having an outer diameter smaller than the outer diameter of the ball bearing may be used. In this case, since the outer race of the ball bearing protrudes in the radial direction from the output gear, the ball bearing interferes and the ring gear of the differential device cannot be engaged with the output gear. For this reason, even if the differential device is installed in the transmission case after the driven shaft with the ball bearing previously attached is installed in the transmission case, the differential device cannot be installed.
The same problem occurs not only when the ring gear of the differential device is meshed with the output gear but also when the reduction gear is meshed with the output gear (in the case of a four-axis configuration).
JP 2002-327828 A

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide an output gear and a ball that do not apply an excessive load to the bearing supporting the other end of the driven shaft when the one end of the driven shaft is supported using a ball bearing. An object of the present invention is to provide an assembling structure and assembling method of a continuously variable transmission capable of rear-assembling a bearing on a driven shaft.

In order to achieve the above object, an invention according to claim 1 is provided with a drive pulley and a driven pulley around which a V-belt is wound, and both ends of a driven shaft supporting the driven pulley are connected to a transmission via a bearing. In a continuously variable transmission that is rotatably supported by a case and has an output gear that meshes with a ring gear or a reduction gear of a differential device fixed to one end of the driven shaft, the output gear is formed on the outer periphery of a cylindrical gear sleeve. A cylindrical extension without a gear portion is formed at one axial end of the gear sleeve, and a ball bearing having an outer diameter larger than the root diameter of the output gear is fitted and fixed to the outer periphery of the extension, An inner spline is formed on the inner periphery of the gear sleeve to be fitted with an outer spline formed on the outer periphery on one end side of the driven shaft, and the gear sleeve is connected to the driven sleeve. The sprocket is engaged with the output gear, the output gear meshes with the ring gear or reduction gear of the differential unit, and the lock sleeve is fastened to the shaft end of the driven shaft to press the gear sleeve in the axial direction. An assembly structure of a continuously variable transmission is provided in which an end portion is pressed against and fixed to a stopper portion of a driven shaft.

According to a second aspect of the present invention, a drive pulley and a driven pulley around which a V-belt is wound are provided, and both ends of the driven shaft that supports the driven pulley are rotatably supported by a transmission case through bearings. In the assembling method of the continuously variable transmission in which the output gear meshing with the ring gear or the reduction gear of the differential device is fixed to one end side of the driven shaft, a cylindrical shape having an output gear on the outer periphery and no gear portion on one end in the axial direction A step of preparing a gear sleeve in which an extension portion of the gear sleeve is formed; a step of fitting and fixing a ball bearing having an outer diameter larger than the root diameter of the output gear to the extension portion of the gear sleeve; A step of supporting the other end of the driven shaft through a bearing, and the differential device and / or the reduction gear is assembled to one of the transmission cases. Engaging the gear sleeve with the ball bearing fitted and fixed to one end of the driven shaft, engaging the output gear of the gear sleeve with the ring gear or the reduction gear of the differential device, and the driven By fastening a lock nut to the shaft end of the shaft, the gear sleeve is pressed in the axial direction, the other end of the gear sleeve in the axial direction is pressed against the stopper portion of the driven shaft, and the speed is changed to the ball bearing. There is provided a method of assembling a continuously variable transmission, comprising the step of fitting the other of the machine cases.

When mounting the ball bearing directly on the driven shaft, the inner race of the ball bearing must be fitted and fixed to the driven shaft before being assembled into the transmission case. When the diameter is larger than that of the gear, the differential device cannot be incorporated into the transmission case.
Therefore, in the present invention, the output gear is formed in a cylindrical gear sleeve, and a ball bearing is fitted and fixed in advance to the extension portion of the gear sleeve.
Next, the driven shaft and the differential device are incorporated into the transmission case, and then the gear sleeve is spline fitted to the driven shaft. At this time, the output gear can be easily meshed with the ring gear of the differential device without being obstructed by the ball bearing.
Next, a lock nut is fastened to the shaft end of the driven shaft, and the gear sleeve is pressed against the stopper portion of the driven shaft and fixed. Thus, the output gear is securely fixed in the axial direction and the rotational direction with respect to the driven shaft. At this time, an axial load is not applied to the bearing provided on the other end side of the driven shaft, and the bearing is not damaged.
Finally, the assembly is completed when the other side of the transmission case is fitted to the ball bearing.

In the case of a continuously variable transmission with a three-axis configuration, the output gear may be meshed with the ring gear of the differential device. However, in the case of a four-axis configuration, a reduction gear is interposed between the output gear and the ring gear of the differential device. In this case as well, the output gear can be converted into a reduction gear by spline-fitting the driven shaft, differential device, and reduction gear incorporated on one side of the transmission case to the driven shaft with a gear sleeve fitted with a ball bearing. It can be easily engaged.

As described above, according to the present invention, the ball bearing is fitted and fixed in advance to the gear sleeve having the output gear, and the gear sleeve is spline fitted to the driven shaft incorporated in the transmission case. Since the output gear is meshed with the ring gear of the differential unit incorporated in the transmission case, the output gear can be connected without being disturbed by the ball bearing even if the outer diameter of the ball bearing is larger than the output gear. Can mesh with ring gear.
Further, since the gear sleeve is fastened to the driven shaft with a lock nut, an axial load is not applied to the bearing supporting the other end of the driven shaft, and the bearing is not damaged.
Further, since the ball bearing is assembled and fixed to the gear sleeve in advance, the output gear and the ball bearing can be fixed to the driven shaft at the same time, and there is an advantage that the assembling workability is improved.

Embodiments of the present invention will be described below with reference to examples.

1 to 3 show an example of a continuously variable transmission according to the present invention.
The continuously variable transmission of this embodiment is an FF horizontal type automotive transmission, which is roughly switched between forward and reverse rotation of the input shaft 3 driven by the engine output shaft 1 via the torque converter 2 and the input shaft 3. The forward / reverse switching device 4 that transmits to the drive shaft 10, the continuously variable transmission A comprising the drive pulley 11, the driven pulley 21, and the V belt 15 wound between both pulleys, the power of the driven shaft 20 is output shaft 32. And a differential device 30 that transmits to the terminal. The input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole.
The V belt 15 used in this embodiment is a known metal belt composed of a pair of endless tension bands and a large number of blocks supported by these tension bands.

Each component constituting the continuously variable transmission is accommodated in a transmission case 5. An oil pump 6 is disposed between the torque converter 2 and the forward / reverse switching device 4. As shown in FIG. 3, the oil pump includes an oil pump body 7 fixed to the transmission case 5, an oil pump cover 8 fixed to the oil pump body 7, an oil pump body 7, and an oil pump cover. 8 and the pump gear 9 accommodated between the two. The pump gear 9 is driven by the pump impeller 2 a of the torque converter 2. The turbine runner 2 b of the torque converter 2 is connected to the input shaft 3.

As shown in FIG. 3, the forward / reverse switching device 4 includes a planetary gear mechanism 40, a forward brake 50, and a reverse clutch 51, and a sun gear 41 of the planetary gear mechanism 40 is connected to an input shaft 3 that is an input member. The ring gear 42 is coupled to the drive shaft 10 that is an output member. The planetary gear mechanism 40 is a single pinion system, the forward brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5, and the reverse clutch 51 is provided between the carrier 44 and the sun gear 41. ing. When the reverse clutch 51 is released and the forward brake 50 is engaged, the rotation of the input shaft 3 is reversed, decelerated, and transmitted to the drive shaft 10. Conversely, when the forward brake 50 is released and the reverse clutch 51 is engaged, the carrier 44 and the sun gear 41 of the planetary gear mechanism 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly connected.

The structure of the forward / reverse switching device 4 will be specifically described. The carrier 44 is provided with a cylindrical portion 44a serving as both a clutch hub of the forward brake 50 and a clutch drum of the reverse clutch 51, and the cylindrical portion 44a protrudes toward the engine side. A brake disc 50a of the forward brake 50 is disposed on the outer periphery of the cylindrical portion 44a, and a clutch disk 51a of the reverse clutch 51 is disposed on the inner periphery of the cylindrical portion 44a. Here, the brake disk 50 includes both a friction disk and a plate member, and the clutch disk 51a includes both a friction disk and a plate member. The piston 50b of the forward brake 50 is operated by hydraulic pressure supplied to a hydraulic chamber 50c formed in the transmission case 5, and the brake disc 50a is fastened by the piston 50b. A cylindrical cylinder portion 8a is integrally projected from an oil pump cover 8 that is a stationary member as a reaction force member that supports the end portion of the brake disc 50a that is pressed by the pressure of the piston 50b.

A cylindrical portion 41a that serves as a clutch hub of the reverse clutch 51 is integrally projected on the engine side of the sun gear 41, and the clutch disk 51a of the reverse clutch 51 is supported on the outer periphery of the cylindrical portion 41a. Yes. A concave hydraulic chamber 51b is formed on the back side of the oil pump cover 8 (side surface facing the forward / reverse switching device 4), and the piston 51c is operated by the hydraulic pressure supplied to the hydraulic chamber 51b. It is concluded. The piston 51c has a U-shaped cross section, and a thrust bearing 52 that allows relative rotation is disposed on the side surface of the piston 51c that faces the clutch disk 51a. Therefore, the axial pressure of the piston 51c is effectively transmitted to the clutch disk 51a, and the piston 51c is prevented from rotating with the clutch disk 51a of the reverse clutch 51. Since the carrier 44 is disposed behind the clutch disk 51a, the end of the clutch disk 51a pushed by the pressure of the piston 51c can be supported by the end surface of the carrier 44.

The drive pulley 11 of the continuously variable transmission A is integrally movable with a fixed sheave 11a integrally formed on a drive shaft (pulley shaft) 10 and axially movable on the drive shaft 10 via a roller spline portion 13. The movable sheave 11b is rotatably supported, and the hydraulic servo 12 is provided behind the movable sheave 11b. A piston portion 12a extending to the back side is integrally formed on the outer peripheral portion of the movable sheave 11b, and the outer peripheral portion of the piston portion 12a is in sliding contact with the inner peripheral portion of the cylinder 12b fixed to the drive shaft 10. A hydraulic oil chamber 12c of the hydraulic servo 12 is formed between the movable sheave 11b and the cylinder 12b, and the shift control is performed by controlling the hydraulic pressure to the hydraulic oil chamber 12c.

The driven pulley 21 is supported by a fixed sheave 21a integrally formed on the driven shaft (pulley shaft) 20 and on the driven shaft 20 via a roller spline portion 23 so as to be axially movable and integrally rotatable. A movable sheave 21b and a hydraulic servo 22 provided behind the movable sheave 21b are provided. The structure of the roller spline portion 23 is the same as that of the roller spline portion 13 of the drive pulley 11. A cylinder portion 22a extending to the back side is integrally formed on the outer peripheral portion of the movable sheave 21b, and a piston 22b fixed to the driven shaft 20 is in sliding contact with the inner peripheral portion of the cylinder portion 22a. A hydraulic oil chamber 22c of the hydraulic servo 22 is formed between the movable sheave 21b and the piston 22b. By controlling the hydraulic pressure of the hydraulic oil chamber 22c, a belt thrust necessary for torque transmission is given. Note that a spring 24 for applying an initial thrust is disposed in the hydraulic oil chamber 22c.

One end portion of the driven shaft 20 extends toward the engine side, and an output gear 27a is fixed to this one end portion. The output gear 27a meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.

Here, the support structure of the driven shaft 20 will be described with reference to FIGS.
As shown in FIG. 1, the rear (non-engine side) end of the driven shaft 20 is rotatably supported by one cover member 5a of the transmission case 5 via a ball bearing 25, and the front side (engine side). ) Is rotatably supported by the other cover member (converter housing) 5b of the transmission case 5 via a ball bearing 26.

As shown in FIG. 4, the output gear 27 a is formed at a substantially central portion of the outer periphery of the cylindrical gear sleeve 27. A cylindrical extension portion 27b having no gear portion is formed at one axial end portion (engine side end portion) of the gear sleeve 27, and an outer diameter D4 larger than the tooth root diameter D1 of the output gear 27a is formed on the outer periphery of the extension portion 27b. The inner race 26a of the ball bearing 26 having the above is fitted and fixed by press-fitting. Here, the outer diameter D2 of the extension 27b is smaller than the root diameter D1 of the output gear 27a, but may be larger than D1. The outer diameter D4 of the ball bearing 26 is larger than the tooth tip diameter D3 of the output gear 27a, but may be smaller than D3. A cylindrical portion 27c having a diameter smaller than the root diameter D1 of the output gear 27a is formed at the other axial end portion of the gear sleeve 27 in the same manner as the extension portion 27b. The end surface of the cylindrical portion 27c is fixed to the driven shaft 20. It is in contact with the back surface of the piston 22b (stopper portion). The cylindrical portion 27c is provided as necessary. An inner spline 27 d that fits with an outer spline 20 a formed on the outer periphery on one end side of the driven shaft 20 is formed on the inner periphery of the gear sleeve 27. A lock nut 28 is fastened to the threaded portion 20b formed at the shaft end of the driven shaft 20, the gear sleeve 27 is pressed in the axial direction by the lock nut 28, and the end surface of the cylindrical portion 27c of the gear sleeve 27 is driven by the driven shaft 20. The piston 22b is pressed against and fixed. The inner side surface of the lock nut 28 may abut against the end surface of the extension portion 27b or may abut against the inner race 26a of the ball bearing 26. The outer race 26 b of the ball bearing 26 is fitted and held in a recess 5 b 1 formed in the other cover member 5 b of the transmission case 5.

Here, a method of assembling the driven shaft 20 and the differential device 30 will be described with reference to FIG.
First, the rear end portion of the driven shaft 20 that supports the driven pulley 21 is assembled to one cover member 5a of the transmission case 5 via the ball bearing 25, and the main body of the transmission case 5 fixed to the cover member 5a. The differential device 30 is assembled to the member 5c. A ring gear 31 is already fixed to the differential device 30. This state is shown on the left side of FIG.
Next, the gear sleeve 27 in which the ball bearing 26 is fitted and fixed in advance is spline fitted to the driven shaft 20 assembled to the cover member 5a of the transmission case 5 as described above. At this time, the output gear 27 a is engaged with the ring gear 31 of the differential device 30. Since the large-diameter ball bearing 26 is located behind the output gear 27a in the insertion direction, the gear sleeve 27 can be smoothly inserted without being obstructed by the ball bearing 26.
Next, the lock nut 28 is fastened to the threaded portion 20 b at the shaft end of the driven shaft 20. The gear sleeve 27 is pushed in the axial direction by the tightening force of the lock nut 28, and the end surface of the cylindrical portion 27 c is pressed against the back surface of the piston 22 b of the driven shaft 20 to be fixed. In this way, the tightening force of the lock nut 28 terminates at the piston 22b and does not affect the other ball bearing 25, so that it is not necessary to apply an extra load to the ball bearing 25.
After fastening the lock nut 28, the other cover member 5 b of the transmission case 5 is fitted to the ball bearing 26 to complete the assembly.

The present invention is not limited to the above embodiments.
In the above embodiment, the output gear 27a is provided at the center of the gear sleeve 27 and the extension 27b and the cylindrical part 27c are provided at both ends in the axial direction. However, the cylindrical part 27c can be omitted.
The stopper portion of the driven shaft 20 that presses against the axial end portion of the gear sleeve 27 is not limited to the piston 22b as in the embodiment. For example, a step portion formed in the middle of the driven shaft 20 is used as the stopper portion. You can also.

It is an expanded sectional view of an example of a continuously variable transmission concerning the present invention. FIG. 2 is a skeleton diagram of the continuously variable transmission shown in FIG. 1. FIG. 2 is a detailed sectional view of the forward / reverse switching device for the continuously variable transmission shown in FIG. 1. It is an expanded sectional view which shows the support structure of a driven shaft. It is a figure which shows the assembly method of a driven pulley. It is sectional drawing which shows the support structure of the driven shaft in the conventional continuously variable transmission.

Explanation of symbols

3 Input shaft 4 Forward / reverse switching device 10 Drive shaft 11 Drive pulley 15 V belt 20 Drive shaft 21 Drive pulley 26 Ball bearing 27 Gear sleeve 27a Output gear 27b Extension portion 28 Lock nut 30 Differential device 31 Ring gear

Claims (2)

A drive pulley and a driven pulley wound with a V-belt are provided, and both ends of the driven shaft that supports the driven pulley are rotatably supported by a transmission case through bearings, and a differential is provided at one end of the driven shaft. In a continuously variable transmission that fixes an output gear that meshes with a ring gear or a reduction gear of the device,
The output gear is formed on the outer periphery of a cylindrical gear sleeve,
A cylindrical extension without a gear part is formed at one axial end of the gear sleeve,
A ball bearing having an outer diameter larger than the root diameter of the output gear is fitted and fixed to the outer periphery of the extension portion,
An inner spline is formed on the inner periphery of the gear sleeve to be engaged with an outer spline formed on the outer periphery on one end side of the driven shaft.
The gear sleeve is spline-fitted to the driven shaft, the output gear is meshed with the ring gear or reduction gear of the differential device, and a lock nut is fastened to the shaft end of the driven shaft to press the gear sleeve in the axial direction. An assembly structure of a continuously variable transmission, characterized in that the other end portion in the axial direction of the gear sleeve is pressed against and fixed to the stopper portion of the driven shaft. A drive pulley and a driven pulley wound with a V-belt are provided, and both ends of the driven shaft that supports the driven pulley are rotatably supported by a transmission case through bearings, and a differential is provided at one end of the driven shaft. In the assembly method of the continuously variable transmission for fixing the output gear meshing with the ring gear or the reduction gear of the device,
Preparing a gear sleeve having an output gear on the outer periphery and having a cylindrical extension formed on one end in the axial direction without a gear;
Fitting and fixing a ball bearing having an outer diameter larger than the root diameter of the output gear to the extension of the gear sleeve;
Supporting one end of the driven shaft of the transmission case via a bearing;
Incorporating the differential device and / or the reduction gear into one of the transmission cases;
Spline-fitting the gear sleeve with the ball bearing fitted and fixed to one end of the driven shaft, and engaging the output gear of the gear sleeve with the ring gear or the reduction gear of the differential device;
Fastening the lock nut to the shaft end of the driven shaft to press the gear sleeve in the axial direction and pressing the other end in the axial direction of the gear sleeve against the stopper portion of the driven shaft;
And a step of fitting the other of the transmission case with the ball bearing.

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